US6053195A - Pressure control valve - Google Patents

Pressure control valve Download PDF

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Publication number
US6053195A
US6053195A US09/173,657 US17365798A US6053195A US 6053195 A US6053195 A US 6053195A US 17365798 A US17365798 A US 17365798A US 6053195 A US6053195 A US 6053195A
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US
United States
Prior art keywords
working chamber
pressure
oil
piston
slide valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US09/173,657
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English (en)
Inventor
Siegfried Heer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
TCG Unitech AG
Original Assignee
TCG Unitech AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by TCG Unitech AG filed Critical TCG Unitech AG
Application granted granted Critical
Publication of US6053195A publication Critical patent/US6053195A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/16—Controlling lubricant pressure or quantity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/18—Indicating or safety devices
    • F01M1/20—Indicating or safety devices concerning lubricant pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2605—Pressure responsive
    • Y10T137/263—Plural sensors for single bypass or relief valve
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2708—Plural sensors
    • Y10T137/271—For single valve

Definitions

  • the present invention relates to a pressure control valve for regulating the oil pressure in an oil supply system, preferably of an internal combustion engine, with a first working chamber which is in connection with an oil line, with a second working chamber which is in connection with an oil supply line, and with a control slide valve which is substantially movable by the oil pressure in the first working chamber, with the control slide valve releasing the throttling aperture when exceeding a first predetermined oil pressure in the first working chamber through which the oil from the second working chamber is released into a recirculation system, and with the control slide valve having a control element formed as a piston which is movable in the axial direction by the oil pressure in the second working chamber relative to a main body of the control slide valve and which on exceeding a second predetermined oil pressure in the second working chamber releases the throttling aperture through which oil from the second working chamber is released into the recirculation system.
  • a known pressure control valve is arranged in such a way that a cylinder chamber is in connection with the main oil duct of the machine, with the oil pressure in the main oil duct moving a control slide valve against the action of a spring.
  • a working chamber in this pressure control valve is in connection with an oil supply line and comprises a throttling edge which is controlled by the control slide valve. If the pressure in the main oil duct exceeds a predetermined value, a control edge of the control slide valve reaches a throttling aperture, so that the oil from the supply line is released into a recirculation system.
  • a pressure control valve in which a piston is arranged in a slide valve.
  • a first control edge is released, whereas an other control valve is released by a movement of the piston.
  • the production of such a valve with the desired precision is complex, particularly with respect to the two control edges.
  • the pressure control valve additionally assumes the function of a pressure relief valve, and makes the same superfluous, without requiring any additional constructional space, and all this with a minimal additional constructional effort as compared with a known pressure control valve.
  • no additional line connections or the like are required by the present invention.
  • a particularly simple constructional realization of the pressure control valve in accordance with the invention is given in such a way that preferably the main body of the control slide valve is provided with a collar which separates the first working chamber from the second one. It is particularly favourable if the control element is arranged as a piston which is movable on a guide rod of the main body in the axial direction with respect to the main body of the control slide valve.
  • the main body is provided with a stop which entrains the piston in the direction of the opening of the throttling aperture.
  • the piston permanently rests on the stop.
  • the piston lift off from the stop in order to thus provide a function of pressure relief.
  • a first spring is arranged between the piston and a supporting area fixed with the valve, whereas a second spring is arranged between the main body and the piston.
  • the first spring is used for resetting the control slide valve in normal operation as pressure control valve.
  • the second spring presses the piston against the stop.
  • the first and second spring are arranged coaxially within one another. This leads to a particuarly compact arrangement of the valve in accordance with the invention.
  • first and second spring above one another, so that the first spring pretensions the main body upwardly, whereas the second spring results in a pretensioning force between main body and piston.
  • the pressure relief function of the valve will be initiated when the pressure in the second working chamber exceeds the pretensioning force of the second spring alone.
  • a further simplification of the structure of the pressure control valve in accordance with the invention is obtained in that the collar and the piston are arranged in a movable way in the axial direction in a common bore.
  • FIG. 1 shows a longitudinal sectional view through a pressure control valve in accordance with the invention in a first working position
  • FIGS. 2 and 3 show further working positions of the pressure control valve of FIG. 1.
  • the pressure control valve consists of a housing 1 in which a cylindrical bore 2 is provided.
  • a control slide valve 3 consists of a main body 4 and a piston 5.
  • a collar 19 of the main body 4 separates a first working chamber 6 from a second working chamber 7.
  • the first working chamber 6 is in connection via a connection 8 with a main oil duct (not shown in closer detail) of an internal combustion engine (also not shown in closer detail).
  • the pressure in working chamber 6 exercises a downwardly directed force onto control slide valve 3 which is proportional to the pressure in the main oil duct.
  • the second working chamber 7 is in connection with an oil supply line via a schematically shown recess 9 through which the internal combustion engine is supplied by an oil pump with lubricating oil. These components are also not shown.
  • a throttling aperture 10 is provided below the opening 9, which aperture is controlled by a control edge 11 of the piston 5.
  • the throttling aperture 10 is in connection with an oil supply recirculation system.
  • a sealing element 12 which is screwed into the cylinder comprises a bearing surface 13 on which a first spring 14 rests.
  • the first spring 14 further rests on the lower side of the piston 5 in order to pretension the same upwardly.
  • a Seeger circlip ring 15 is further attached at the lower end of the main body 4 of the control slide valve 5, which ring carries a supporting ring 16.
  • a second spring 17 rests on the supporting ring 16, which spring also pretensions the piston 5 upwardly.
  • FIG. 1 shows a state in which the pressure of the main oil duct is below a predetermined setpoint value.
  • the pressure in the oil supply line is also below a predetermined maximum value which is higher than the setpoint value in the main oil duct. Therefore the pressure in the first working chamber 6 is insufficient to press the slide valve 3 downwardly against the resistance of the first spring 14. In the same way, the pressure in the second working chamber 7 is insufficient to lift off the piston 5 from the stop 18. For these reasons the piston 5 is disposed in its upper end position in which the throttling aperture 10 is closed.
  • FIG. 2 shows a case which corresponds to a cold start at extremely low temperatures.
  • the pressure in the oil supply line is very high, but as a result of the flow resistances the pressure in the main oil duct has not risen to the extent so as to downwardly move the slide valve 3 of the pressure control valve.
  • the high pressure in the second working chamber 7 causes the piston 5 to lift off from stop 18 against the pretensioning forces of the first and second spring 14 and 17 in order to slide downwardly on the main body 4 of the control slide valve 3.
  • FIG. 3 shows a state in which the pressure in the main oil duct has reached or exceed a predetermined setpoint value, whereas the pressure in the oil supply line moves within the permitted range.
  • the oil pressure in the first working chamber 6 multiplied with the cross-sectional area of the collar 19 of the control slide valve 3 leads to a force which exceeds the pretensioning force of the first spring 14.
  • the control slide valve 3 is moved downwardly to such an extent that the control surface 11 of the piston 5 releases the throttling aperture 10.
  • oil is released from the oil supply line via the throttling aperture 10 for such a time until the pressure in the main oil duct has reached the setpoint value or falls below the same.
  • a ventilation opening 20 is used for ventilating the space below the piston 5 in which springs 14 and 17 are arranged.
  • the present invention substantially corresponds in a constructional respect to a known pressure control valve.
  • the piston 5 is movably arranged relative to the main body 4 of the control slide valve 3 and that the second spring 17 is provided for pretensioning the piston 5 against the main body 4 of the control slide valve 3.
  • the control slide valve 3 must be arranged in accordance with the invention. In this way it is possible to achieve an additional function with minimal effort which allows omitting an other component, namely a separate pressure relief valve.
  • the particularly advantageous aspect is that the additional function does not cause any increase in installed size and thus no additional weight.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Magnetically Actuated Valves (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Valve Device For Special Equipments (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Driven Valves (AREA)
US09/173,657 1997-10-16 1998-10-16 Pressure control valve Expired - Fee Related US6053195A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0175997A ATA175997A (de) 1997-10-16 1997-10-16 Druckregelungsventil
AT1759/97 1997-10-16

Publications (1)

Publication Number Publication Date
US6053195A true US6053195A (en) 2000-04-25

Family

ID=3520392

Family Applications (1)

Application Number Title Priority Date Filing Date
US09/173,657 Expired - Fee Related US6053195A (en) 1997-10-16 1998-10-16 Pressure control valve

Country Status (5)

Country Link
US (1) US6053195A (de)
EP (1) EP0909884B1 (de)
AT (2) ATA175997A (de)
DE (1) DE59800463D1 (de)
ES (1) ES2154933T3 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160319700A1 (en) * 2015-04-29 2016-11-03 Alstom Technology Ltd System and method for regulating pressure for a turbomachine
US20170234176A1 (en) * 2016-02-11 2017-08-17 SLPT Global Pump Group Automotive lubricant pumping system with two piece relief valve

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2767726A (en) * 1953-06-23 1956-10-23 Westinghouse Air Brake Co Pilot actuated compensating pressure regulator
US4062374A (en) * 1974-05-08 1977-12-13 Sperry Rand Limited Hydraulic valves and hydraulic systems
US4139015A (en) * 1975-09-25 1979-02-13 Toyota Jidosha Kogyo Kabushiki Kaisha Hydraulic pressure control device for use in automatic transmission
SU969922A1 (ru) * 1978-05-04 1982-10-30 Центральный Ордена Трудового Красного Знамени Научно-Исследовательский Автомобильный И Автомоторный Институт Система смазки двигател внутреннего сгорани

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2456524A1 (de) * 1974-11-29 1976-08-12 Kloeckner Humboldt Deutz Ag Druckumlaufschmieroelanlage fuer brennkraftmaschinen
FR2543615B1 (fr) * 1983-03-30 1987-05-15 Renault Dispositif de regulation de pression, notamment pour pompe a huile de moteur a combustion interne
FR2556775B1 (fr) * 1983-12-20 1988-02-05 Citroen Sa Dispositif de limitation de la pression dans un circuit de lubrification de moteur
FR2705403B1 (fr) * 1993-05-14 1995-06-23 Renault Dispositif de limitation de la pression dans un circuit de lubrification de moteur.

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2767726A (en) * 1953-06-23 1956-10-23 Westinghouse Air Brake Co Pilot actuated compensating pressure regulator
US4062374A (en) * 1974-05-08 1977-12-13 Sperry Rand Limited Hydraulic valves and hydraulic systems
US4139015A (en) * 1975-09-25 1979-02-13 Toyota Jidosha Kogyo Kabushiki Kaisha Hydraulic pressure control device for use in automatic transmission
SU969922A1 (ru) * 1978-05-04 1982-10-30 Центральный Ордена Трудового Красного Знамени Научно-Исследовательский Автомобильный И Автомоторный Институт Система смазки двигател внутреннего сгорани

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160319700A1 (en) * 2015-04-29 2016-11-03 Alstom Technology Ltd System and method for regulating pressure for a turbomachine
US9976445B2 (en) * 2015-04-29 2018-05-22 General Electric Technology Gmbh System and method for regulating pressure for a turbomachine
US20170234176A1 (en) * 2016-02-11 2017-08-17 SLPT Global Pump Group Automotive lubricant pumping system with two piece relief valve
US10392977B2 (en) * 2016-02-11 2019-08-27 Slw Automotive Inc. Automotive lubricant pumping system with two piece relief valve

Also Published As

Publication number Publication date
ES2154933T3 (es) 2001-04-16
EP0909884B1 (de) 2001-02-07
EP0909884A1 (de) 1999-04-21
ATE199106T1 (de) 2001-02-15
DE59800463D1 (de) 2001-03-15
ATA175997A (de) 2002-02-15

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LAPS Lapse for failure to pay maintenance fees
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Effective date: 20040425

STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362